Variable and reversible flow pump



H. J. BUSH VARIABLE AND REVERSIBLE FLOW PUMP Jan. 3, 1950 Filed April 10, 1946 3 Sheets-Sheet l ENTOR.

Harry J. Bush A'I'I'El RN EYE .Jan. 3, 1950 J, BUSH 2,493,525

VARIABLE AND REVERSIBLE FLOW PUMP Filed April 10, 1946 s Sheets-Sheet 2 6O INVENTOR.

82 Harry J. Bush ATTD RN EYS Jan. 3, 1950 H. J. BUSH VARIABLE AND REVERSIBLE FLOW PUMP Filed April 10, 1946 3 Sheets-Sheet 3 INVENTOR. Hairy J. Bush A'ITD RN EYB Patented Jan. 3, 1950 UNITED STATES PATENT OFFICE 2,493,525 VARIABLE AND REVERSIBLE FLOW PUMP Harry J. Bush, Wilmington, Del. Application April 10, 1946, Serial No. 660,977

6 Claims.

This invention relates to improvements in rotary, vane type pumps and the primary object of the invention is to provide a positive pump which merely by manipulation of the pump housing will pump varied volumes of gas or fluid containing a lubricant in a forward or reversed direction, while the rotor of the pump continues to turn in the same direction at the same speed, and in which the rotor may be turned in either clockwise or anti-clockwise direction at constant or varied speeds.

Another object of the invention is to provide a pump which when forced to receive a gas or fluid containing a lubricant will act as a positive motor, in which the direction and speed at which the rotor turns can be controlled merely by manipulation of the pump housing and Without necessarily changing the volume or direction of fluid flow to the pump.

The pumping unit can be used alone for pumping of any liquids to any given pressure in either direction Without the use of valves. The unit being constructed of materials impervious to liquids being handled. In this capacity of operation a manually adjustable control with overload spring would be used.

The pumping unit can be used to supply hydraulic force for presses up to almost any pressure. In this case the unit could be controlled by a lever for manual control and overload springs could be used to control maximum pressure. Speed of the press with which the unit is used would depend on the size of the pump.

The pumping unit may be used to drive the receiving unit, which in turn would be used to drive stationary machinery or mobile equipment, such as cars, trucks, buses or similar vehicles. For such application the units may be set at an angle to each other, any ratio between the units can be obtained. Maximum volume between units can differ i. e., where a special ratio range is required, such as in driving heavy, light, fast or slow machinery. In this capacity the units would be acting as a variable speed reducer or increaser.

The pumping and receiving units may be built into a single compact unit, affording any increased or decreased ratio, without the use of flexible connecting hoses and the pump flow may or may not be reversible as desired.

With the above and other objects and applications in view the invention consists of the novel details of construction, arrangement and combination of parts more fully hereinafter described,

claimed and illustrated in the accompanying drawings in which:

Figure 1 is an elevational view of an embodiment of the invention partlybroken away;

Figure 2 is a sectional view on the line 2-2 of Figure 1 with the control mechanism removed;

Figure 3 is a vertical section of the pump with the rotor in position for forward flow;

Figure 4 is the same with the rotor in clockwise travel and neutral position;

v Figure 5 is the same with the rotor in position for reverse flow; 7

Figure 6 is an elevational view partly in section of a pumping unit, receiving unit and control therefore; Figure '7 is a sectional view on the line I- of Figure 4; and

Figure 8 is an elevational view of a pumping unit. a

Referring more in detail to the drawings the numeral l0 designates the pumping unit which comprises the housing l2 which is provided at its top and bottom periphery with apertured, en-v largements l4 and I6 respectively. A pin I8 mounts the housing I2 by insertion in the enlargement H5 -in the fulcrum 20 of the base 22 and the base 22 has upturned ends 24 and 26 respectively to mount the bolts 28 which limit the maximum movement of the housing on the pin 18 and nuts 30 retain the bolts 28 in any desired position. The base 22 is secured to a suitable support 32 bypbolts 34 and a depression 36 in alignment with the bolt 28 in the end 26 permits full movement of the bolt as desired.

A hanger 38 is mounted on the enlargement M by means of the pin 40 and an overload spring 42 mounted on the rod 44 is carried by the hanger 38. The rod 44 is threaded at 46 and 48 to receive the pressure adjustment nuts 50 and the threaded portion. 46 is receivable in the complementary threaded bracket 52. A handle 54 secured to the free end of the portion 46 and retained thereon by nut 56 controls the pivotal movement of the housing on the fulcrum 20 of the base. 7

The housing I2 is provided with the circular working chamber 58 in which therotor 60 is mounted and is suitably connected in driving relation with the shaft 62 by the key 64. The shaft 62 is a drive shaft from any suitable power plant 66 which is secured by bolts 68 to the support 32. The rotor 60 is provided with diverging open ended slots 10 in which are slidably mounted the impeller vanes 12. It will be noted from Figures 3 to 5 inclusive that the vanes are in sections and are free to move independently of each other within the slots and are held in constant contact with the wall of the chamber 58 at all times by the springs 14 which engage the inner end of the slots and the innerends of the vanes. It will also be noted that the ends of the sections are inclined downwardly from the center thereof.

The housing I2 is provided with nozzles 16 which are threadedto receiveflexible pipe adapters I8 and passages Q80 and 82 .respectively communicate with the working chamber 58 by means of ports 84 and the housing is provided with a removable cover plate 86 secured thereto by bolts 88.

The cover plate is bevelled at 98 to prevent leakage and sufilcient clearance. is provided between the plate and rotor for lubricating purposes.

The seal for the housing I2 comprises the circular shell 92 and fixed rear seal plate 94 against which the rotating seal 96 bears by reason of the spring 98 which engages at one end the seal cap washer I08 which engages the seal washer I82 which engages the seal 96, the other end of the spring-98, engages the thrust bearing I84 which bears against the flat washer I86 which prevents the thrust bearing from entering the clearance I88 between the housing I2 and shaft 62 and the thrust bearing prevents friction between the spring 98 and washer I06 and all seal parts rotate except the plate 94 and washer I86. The seal would'be a carbon or metal seal backed up by a rubber seal which is in turn backed up'by a cup and spring. The'spring holds a tension on the seal parts against the removable fixed seal plate which is made of a hard polished metal with a soft wearing surface andthe seal plate has clearance H8 around the shaft and the shell 92 has clearance around the sealto allow for shell movement and since the drive shaft carries the rotor no bearings are required in this unit.

, The rotor 68 which is smaller than the working chamber 58 rotates at a speed of driving shaft 62 within the chamber of the housing I2. When the housing I2 is centered on the rotor as shown in Figure 4, no fluid is being displaced due to equal clearance between all points I of the rotor and housing, and even if the rotor was turning no fluid would be displaced.

. With the rotor 6.8 turning on a constant axis the top of the housing is moved from a vertical center, creating unequal clearance between the rotor and housing. With the rotor turning in clockwise direction and the housing moved to the left as shown in Figure 3, fluid would be drawn in passage 82 and be carried by vanes 12 around the chamber 58 to passage 80 and forced outwardly thereof. Therefore the further off center the housing is moved the greater the volume of fluid displaced. V V

If the housing is moved tothe rightas shown in Figure 5, the'direction of the flow of liquid will be reversed since the clearance of the rotor and housing at the ports determine the flow of the liquid. Thus the direction of the flow of the liquid is changed while the rotation ofv the rotor is constant in the same direction. V In Figure l one method .of controlling the housing is shown but othermethods can be used as desired and the annular distancebetween the passages 88 and 82 must not be greater than the annular distance between the points oftwo succeed: ing vanes. .The clearance between the fixed seal and shell permit movement of the housing about thesha-ft. i 4 i F In Figure 6 the pumping'unit lll is connected 4 by flexible couplings H2 to the receiving unit II4 which is constructed in like manner as is the pumping unit having the housing II6 a Working chamber I I8 rotor I20, slots I22, two piece vanes I24, springs I26 and the shaft I21. The housing has the removable cover I28 secured by bolts I30 and inlet I32 and outlet I34 all other elements not shown would be of the same construction as previously described, for the,, pumping unit. However, in this instance the hanger 38 is connected to a lever' I35 pivoted at'l'3'8to a link I38 pivoted at I48 to a suitable support I42 and at I44 to an a' vacuum cylinder I58 mounted on a suitable support I52. Passages I54 and I58 leading from fold of an internal combustion engine. A valve I62 having a lever ltd thereon will connect ports I86 in the valve housing I58 to control the flow of the fluid in the pumping unit by action on the diaphragm of the cylinder I58. V

This set up could be used for cars, trucks, buses or similar vehicles, and the cylinder I58 being controlled by the accelerating pedal of the vehicle would cause movement of the pump housing I2 and subsequent output of thepumping unit.

With engine idling the Vacuum cylinder would exert no force and action of rotor would hold the housing I2 in vertical or center position.

A slight depression of the accelerating pedal would cause the vacuum cylinder to exert a slight force on the housing I2 thereof causing pumping action.

The greater the depression of the pedal the stronger the vacuum pull. The vacuum pull will be balanced by the pressure on the outlet side against the rotor under any and all conditions.

If the vehicle were climbing a hill outlet force would overcome vacuum force because even if vacuum cylinder actuation isfull the manifold vacuum on any engine drops when engine is under a strain. Therefore, the ratio between pump and receiving units would automatically be increased to the point where the engine would maintain proper manifold vacuum. When the strain is eliminated theiratio will automatically reduce to normal.

In Figure 8 the shaft I68 carrying the rotor is separate from the drive shaft, not shown, and the shaft I 68 is journalled in bearings I18 on bearing brackets I12 mounted on a suitable support I14 and seals I16 are provided on ,both sides of the housing I2, a suitable coupling I18 on the end of the shaft i88 is provided for connecting the shaft to a drive shaft.

Thus a pumping unit has been provided that can be controlled manually .or automatically, can be mounted directly on a drive shaft or have coupling therewith and can be used with stationary machines or in motor vehicles.

It is believed that the operation and construction of the invention will be apparent to those skilled in the art and it is to be understood that changes in the details of construction, arrangement and combination of parts may be resorted to provided they fall within the spirit .of the invention and the scope of the appended claims.

I-Iaving thus described the invention what is claimed as new and-desired tobe secured by LettersPatent is:

1. A device of the character described, comprising a base, a body pivoted on said base, upturned opposed 'endson said base, means on the upturned ends of said base for limiting the 'move- 5. ment of said body, a working chamber in said body, liquid inlet and outlet ports for the working chamber, a rotor mounted in said body, sectional vanes mounted in said rotor, spring elements acting on said vanes to displace the vanes outwardly to engage the walls of the working chamber and means for moving said body on its pivot to increase and decrease the clearance of the rotor with the said working chamber, whereby the volume and direction of flow of liquids through said body is changed depending upon the movement of said body to the right or left of the vertical plane of said body.

2. The invention as in claim 1 wherein a power unit having a drive shaft is mounted adjacent said base and said rotor is mounted on the drive shaft of the power unit.

3. The invention as in claim 1 wherein automatic vacuum means is provided for moving said body on its pivot.

4. The invention as in claim 1, wherein a sealing means having a fixed part and a rotary part is provided for said body.

5. The invention as in claim 1, wherein a sealing means is provided having a fixed part mounted on said body, a central opening in said fixed part having a greater circumference than said shaft, a rotating disc seal in said body on said shaft closing the central opening of said fixed part, and a spring on said shaft engaging said rotary disc to force said disc into constant contact with said fixed part.

6. A pumping device comprising a base, a pump body having a circular pump chamber and a pair of fluid passages communicating therewith, pivot means attaching said pump body to said base for oscillatable movements relative thereto, means on said base limiting oscillatable movement of said pump body, said pump body having an elongated opening communicating with said pump chamber and including the geometric axis thereof, a driving shaft extending through said elongated opening and into said pump chamber, a source of power anchored to said base and drivingly supporting said driving shaft, an impeller rotor drivingly secured to said shaft and rotatably mounted within said pump chamber, said rotor having a predetermined diameter less than that of said pump chamber whereby said pump body can be displaced relative to said rotor, said rotor being provided with a plurality of radial slots, impeller vanes slidably mounted in said slots, spring means in said slots forcing said vanes radially outward against the pump chamber periphery, control means for shifting said pump body on said pivot means relative to said shaft for selectively displacing the pump chamber axis to either side of the rotor axis whereby the quantity of fluid and its direction of relative flow through said passages is controlled, and means carried by said driving shaft and pump body sealing said elongated opening against fluid leakage from said pump body along said shaft.

HARRY J. BUSH.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 2,208,074 I-Iolz July 16, 1940 FOREIGN PATENTS Number Country Date 120,879 Switzerland June 16, 1927 227,067 Great Britain Jan. 8, 1925 330,617 Italy Oct. 21, 1935 

